Hydraulic change speed and reversing gear



Jan. 7, 1941. M. CARTER HYDRAULIC CHANGE SPEED AND REVERSING GEAR 6 Sheets-Sheet 1 Filed Nov. 24, 1936 INVENTOK.

Jan. 7, 1941. M. CARTER 2,227,631

HYDRAULIC CHANGE SPEED AND REVERSING GEAR Filed Nov. 24, 195 6 Sheets-Sheet 2 FIGS.

INVENTORQ Jan. 7, 1941. M. CARTER 2,227,631

HYDRAULIC CHANGE SPEED ANDREVERSING GEAR FiledNov. 24, 1936 6 Sheets-Sheet 3 FIG. 6.

INVENTOR.

Jan. 7, 1941. M. CARTER 2,227,631

HYDRAULIC CHANGE SPEED AND REVERSING GEAR Filed NOV. 24, 1936 6 Sheets-Sheet 4 INVENTOR.

Jan. 7, 1941. M. CARTER 2,227,631

HYDRAULIC CHANGE SPEED AND REVERSING GEAR Filed Nov. 24, 1936 6 Sheets-Sheet 5 -FIG. IO.

FIG.

. 0 10 INVENTOR. flaw/1 c: KM

Jan. 7, 1941. M, AR ER 2,227,631

HYDRAULIC CHANGE SPEED AND REVERSfNG GEAR Filed Nov. 24, 1936 26 Sheets-Sheet 6 HG. I2.

INVE N TOR; jwg [M 55 vanes on the eccentric rings.

Patented Jan. 7, 1941 Q PATENT OFFICE HYDRAULIC CHANGE srnnn AND anvnnsmo Gm mm... Carter, Bradford, England Application November 24, 1936, Serial No. 112,569 In Great Britain December 8, 1935 4 Claims. (C1. 60-53) This invention relates tohydraulic change speed and reversing gear of the type consisting of a pump and motor each having pistons or vanes carried in radial cylinders or slots in the pump 5 and motor bodies and in which the pump body is driven by the driving shaft, the motor body being carried in a non-rotatable manner by some fixed part of the gear case, and two eccentric rings or members which cause the pistons or vanes to o reciprocate in their cylinders, or slots being connected to the driven shaft, means being provided for varying the strokes of the pistons or vanes of the pump and motor simultaneously.

The present invention has for its object to introduce an improved construction of gear of the above type in which fluid friction will be reduced to a minimum and which will combine mechanical strength, durability and low friction losses.

According to this invention the two eccentric members which cause the pistons or vanes of the pump and motor to reciprocate encircle the pump and motor discs, or bodies and are mounted in and rotated with a rotatable case which is carried independently of the driven shaft on bearings mounted in a fixed case or frame, a connection capable of transmitting torque being made between the rotatable oase and the driven shaft,- a single distributing valve controlling the flow of liquid to and from the motor and pump cylinders revolving inside the pump and motor bodies and being integral with or connected to the driven shaft. The distributing valve is made of small diameter with consequent low friction losses and p it is formed with two sets of ports, one set of ports controlling the fiow of working fluid to and from the pump cylinders and the other set of ports controlling the flow of working fluid to and from the motor cylinders. The two sets of ports are interconnected by passages within the valve. Each set of ports may be formed by cutting two diametrically opposed ports in the circular section of the valve, leaving the dividing wall between the two ports in the form of an 8 section wall separating the other set of ports. This wall en- 4 sures ample passage area for the working fluid along with mechanical strength of the valve. The two eccentric rings which cause the pistons or vanes of, the pump and motor to reciprocate, encircle the pump and motor discs, or bodies and are mounted in and rotated with a rotatable case which is carried independently of the driven shaft on bearings mounted in a fixed case or frame thereby relieving the bearings of the driven shaft of the loads due to the reactions of the pistons or The rotatable case nected together and may be pivotally mounted in 10 the rotatable case and adjusted for eccentricity by a control member in such a manner that when the eccentricity of either ring is at zero, the eccentricity of the other ring has a magnitude hereinafter referred to as nominal maximum eccentric- I ity used in gears not required to give overdrive or reverse. The driven shaft may be driven in a reverse direction by further adjustment of the eccentric rings beyond the zero position. It may also be driven at a speed that exceeds that of the 20 driving shaft by further adjustment of the eccentric rings beyond the nominal maximum speed position. Adjustment of the two eccentric rings may be obtained by means of axial movement of a control sleeve slidably mounted in a fixed casing. 25 I The invention also comprises the use of a ball bearing mounted in a sleeve slidably mounted in a fixed casing in the dual capacity of a journal bearing for the rotatable case and a thrust hearing for the control sleeve which ensures good sup- 30 port for the rotatable case, reduces the overall length of the gear and cheapens construction.

The invention further includes hydraulic change speed and-reversing gear having the additional features described below and specified in $8 the claims.

In the accompanying drawings- Fig. 1 is a sectional elevation of one form of gear employing piston type pump and motor inaccordance with: the invention. The section is 4' taken on line ll of Fig. 2.

Fig. 2 is a sectional end elevationtaken on line 2-2 of Fig. 1 looking in the direction of the arrow.

, Fig. 3 is a sectional end elevation of the internal parts of the gear shown in Fig. 1 taken along line 5 3-4.

Fig. 4 is an end elevation of the driving arm of the gear shown in Figs. 1 and 2, the enlarged portion of the valve and the fulcrum pin being shown in section. 50

Fig. 5 is a sectional end elevation taken on-line 5-5 of Fig. 1 looking in the direction of the arrow and in which all parts outside the eccentric ring are not shown. I r

Fig. 6 is a sectional elevation of another form of gear employing piston type pump and motor in accordance with the invention. The section is taken on line 6-6 of Fig. 7.

Fig. 7 is a sectional end elevation taken on line 6 'll of Fig. 6 looking in the direction of the arrows.

Fig. 8 is a sectional "plan showing only the eccentric rings and bearings and part of the stroke control mechanism of the gear shown in 10 Figs. 6 and 7. v

Fig. 9 is an end elevation of the driving arm of the gear shown in Figs. 6 and 7, the enlarged portion of the valve and the fulcrum pin being shown in section.

15 Fig. 10 is a sectional elevation taken on line Ill-l of Fig. 11 of one form of gear employing vane type pump and motor in accordance with the invention. Part of the stroke control mechanism is not shown.

99. Fig. 11 is a sectional end elevation taken on line I l-ll of Fig. in which all'parts outside the eccentric ring are not shown.

Fig. 12 is a longitudinal section of one form of distributing valve.

25 Fig. 13 is a longitudinal section of another form of distributing valve.

Fig. 14 is a cross section of the distributing valve taken on line |4l4 Fig. 12 and Fig. 13.

Fig. 15 is a cross section of the distributing 30 valve taken on line l5-|5 Fig. 12 and Fig. 13.

In one form of construction for carrying the invention into effect and as illustrated in Figs. 1 to 5 and 12.14 and 15 a driving shaft I is formed or provided at one end with a valve casing 35 2 to receive a portion of a distributing valve3 which valve is formed with two sets of interconnected ports and forms part of or is fixed to the driven shaft 8. Extending around the valve casing 2 and fixed thereto or formed in a piece 40 therewith is a disc 9 hereinafter referred to as the pump disc. This disc has a number of radial cylinder bores I!) which communicate with ports I l in the .valve casing 2 and such ports co-operate with one set of ports 4 and 5 in the dis- 45 tributing valve 3.

The other set of ports 6 and 1 in the valve 3 co-operates with ports I2 in a valve casing l3 that is formed in a stationary sleeve or bush H in which the driven shaft 8 is free to revolve.

59 Attached to or forming part of this valve casing I3 is a disc l5 hereinafter referred to as the motor disc. This disc has a number of radial cylinder bores l6 which communicate with ports H2 in the valve casing i3.

55 Each pair of ports 4,5 and 6, 7 in the distributing'valve 3 are separated by 8 section walls, Figs. 14 and 15 each wall serving to separate one port of a pair from the other and one 8 section wall being inversely arranged to the other.

60 Port 5 is connected to port 6 by a longitudinal passage l'i within the valve. 3. Port 4 is connected to port I by a longitudinal passage I6 within the valve 3.

These sets of ports and passages 5, l1, 6 and 4,

65 I8, 1 form the means by which the flow of the working fluid between the pump and motor cylinders is controlled. Referring to Fig. 14 and assuming that oil or other working fluid is being delivered by the pump through port 5 into pas- 0 sage I1, the cross sectional area of port 5 is gradually increased from point P to section QQ near passage l1, being everywhere approximately proportional to the volume of fluid passing the section in a given time thus giving an approxi- 7 mately constant velocity of flow of the liquid and leaving a maximum strength of valve section.

This shape of port 5 along with a similar shape of port 4 leaves the metal of the valve 3 in the form of the S shaped wall previously referred to.

Each of the pump cylinders I6 is fitted with a piston l9 that is attached by a short connecting rod and pin 2| to a curved slipper 22, the connecting rod being fixed to or part of the slipper. The outer surfaces of these slippers 22 engage the inner race 23 of a ball or roller bearing that en circles the pump disc 9. The slippers 22 are kept in position by retaining ring 24 which are positioned at opposite sides of the pump disc 9 by flanges on the slippers 22. The outer bearing race 25 is housed in a ring 26.

Each of the motor cylinders I6 is fitted with a piston 21 that is attached by a short connecting rod 28 and pin 29 to a curved slipper 30, the connecting rod being fixed to or part of the slipper.

The outer surfaces of these slippers 36 engage the inner race 3| of a ball or roller bearing that encircles the motor disc l5. The slippers 36 are kept in position by retaining rings 32 which are positioned at opposite sides of the motor disc l5 by flanges on the slippers 30. The outer bearing race 33 is housed in a ring 34.

The two rings 26 and 34 are rigidly fixed together in such a manner that they are eccentric to or out of line with one another. The rings so fixed are housed within a rotatable casing formed of three parts, the front cover 35 of the rotatable casing 36 and back cover 31 being secured by screws 38 Fig. 3 or other suitable means. The rings 26 and 34 are attached to the rotatable casing by a pin 39 which acts as a fulcrum on which the rings can be moved within the rotatable casing. These rings 26 and 34 are attached together by another pin 40 which acts as a means of adjusting their position. For this purpose pin 40 projects through an opening 4| in the front cover 35 of the rotatable casing 36 and is formed with two flats to engage a fork in an arm 42 that projects from a sleeve 43 that is slidably mounted on a tubular boss 44 formed on the front cover 35 of the rotatable casing 36. A portion of the arm 42 is formed with inclined surfaces 45 to engage correspondingly inclined surfaces 46 in the open ends of a ring 41 that is attached to the front cover 35 of the rotatable casing 36. When the sleeve 43 is moved in an endwise direction the inclined surfaces 45 and 46 impart a slight turning movement to the arm 42 relatively to the rotatable casing 35, 36, 3i and so adjust the cocentricities of the rings 26, 34 in relation to the axis of the driving shaft 1 and the driven shaft 6.

Fixed on the slidable sleeve 43 is the inner member of a ball race 48, the outer member of which 49 fits within a control sleeve 56 that is slidable in a tubular boss at one end of a stationary case 5| that encloses the rotatable case and other working parts. The sleeve 50 is attached to an inner sleeve 52 that is formed with rack teeth 53 to engage a pinion 54 that passes through a slot 55 in the control sleeve 50. The pinion 54 is secured to a shaft 56 which is carried in bearings in the stationary case 5 I. The pinion may be feature ensures good support for the rotatable case, short overall length of the gear and cheapens construction.

v The other end of the rotatable case 35, 35, 31 is supported by a ball bearing the outer race of which 53 is housed in the back cover 31, the inner race 53 being fixed on a stationary'member 53 which comprises a flanged bush that isattached to a cover plate ii that closes the end of the stationary casing 5|. This stationary member 33 is keyed to the combined sleeve l4 and valve casing l3 that surrounds the driven shaft 3.

' A connection is made between the rotatable case 35, 35, 31 and the driven shaft 3 so that the two revolve together. For this purpose the distributing valve 3 which is attached to or forms a part of the driven shaft 3 is formed with a ortion of enlarged diameter 3 to which is keyed or otherwise secured a driving device 52 which may be formed with three arms two of which pass between the ball races 23, 25 and 3|, 33 and act as balancing and spacing arms and the third acts as a driving arm by the engagement of a fork formed on it with flats formed on the pin 33 that connects the rings 25 and 34 with the rotatable case 35, 36, 31. This form of connection ensures that the loads on the rotatable case due to the reactions of the pump and motor are not transmitted to the valve 3.

One of the longitudinal passages IS in the distributing valve 3 which constitutes the suction passage of the pump is extended along the driven shaft 3 and communicates with a lateral passage 53 formed therein. The passage 33 may be only open to one side of the driven shaft as shown in full lines Fig. 12 or may be open to both sides of the shaft as shown by dotted lines. This passage 33 leads to an annular space or chamber 54 formed in the stationary bush or sleeve l4 and working fluid is fed into this chamber to make up any loss from the system. For this purpose the chamber 64 is connected by a passage 65 and pipe 63 with a reservoir for the working fluid in the stationary casing 51.

The driving shaft l is supported in one bearing 51 mounted in the front cover of the rotatable casing 35 and another bearing 53 mounted in a cover 33 that is attached to the stationary casing ii. The stationary casing may be fitted with filler cap I0 and gauge H for checking the level of the working fluid. The cylindrical portion 35 of the rotatable casing is fitted with a balance weight 12 calculated or designed to balance about 80% of the out of balance force at top speed, the out of balance force at low speeds being negligible.

Referring to Figures 1, 2 and 5, the two rings 26 and 34 are fixed together so that they are eccentric to or out of line with one another, and the radial distance from the axis of the gear to the center of gravity of these two rings together with the large ball bearings 23-25 and 3i--33 is the arithmetic mean of the radial eccentricities of the two rings 26' and 34.

Referring to Figures 2 and 5 which show the gear in its maximum speed position, this center of gravity is situated to the right of the center line, and the radial distance from the axis of the gear to the center of gravity is half the radial axis of the gear being the same as it is in the maximum speed position.

The out of balance centrifugal force on the two rings and ball bearings is proportional to the radial distance from the axis of the gear to their center of gravity multiplied by the output speed squared.

This out of balance force varies from a high value to the right at maximum speed droppin to zero at half speed, followed by low values to the left at lower speeds and reaching zero again at zero speed.

At maximum speed about 80% of this out of balance force is balanced, as by the fitting of a balance weight I2, Figs. 2 and '1, and by this means the resultant out of balance force is reduced to a value which is not detrimental over the full range of output speeds because although the centrifugal force on the balance weight acts in the same direction as the out of balance force at low speeds the magnitude of the forces is small because of the low speed.

To operate the gear the stationary casing 5! is supplied with a predetermined quantity of oil or other working fluid. The driving shaft I is rotated from any convenient source of power thus driving the pump disc 3. Assume the drive to be in a clockwise direction when viewing Figs. 2 to 5. If the ring 23 that encircles the pump disc 3 is set to its nominal maximum degree of eccentricity relatively to the driving shaft I as shown in Fig. 2, the other ring 34 that encircles the motor disc l5 will be concentric with that disc as shown in Fig. 5 and no motion.of the motor pistons 21 in the cylinders l3 will take place as the ring 34 is carried round the fixed motor disc [5 by the rotatable case 35, 33, 31. Assuming that cylinders 13 and I3, ports 4, 5,3 and I and passages l1 and II are all charged with working fluid, as the pump disc 3 revolves a pressure will be created in those cylinders l3 whose ports II are opposite port 5 in valve 3. This pressure will be communicated along passage I! to port 3 but since no movement of pistons 21 takes place in cylinders 13 no fluid can pass from this port. Working fluid is therefore trapped in some of the cylinders l3 and a direct drive (less slip caused by leakage of the working fluid through the system) is transmitted by means of pistons l3 connecting rods 23, slippers 22 and bearing 23, 25 to the ring 25 that encircles the pump disc 3. Since the two rings 23 and 34 and the rotatable case 35, 33, 31 are all connected by pin 33 all these parts are driven in a clockwise direction. This drive is transmitted to the driven shaft 3 by means of pin 33 driving arm 52 and valve 3 to which the driving arm 32 is attached at 3'.

Figs. 1, 2, 3 and 5 all illustrate the gear in the control position described above which, neglecting slip, gives equal speeds of driving and driven shafts and there is no flow of working fluid.

If the control sleeve 53 is moved axially to the left in Fig. 1 to its other nominal extreme position taking with it the ball bearing 43, 43 and the sleeve 43, the engagement of the inclined faces 45 and 43 on the arm 42 and the ring 41 respectively will cause the arm 42 to move through a small angle carrying pin 43 to the left hand side of the vertical centre line in Figs. 2, 3, and 5.

, In this position of pin! the ring 23 that encircles the pump disc 3 is'"concentric with that disc and the ring 34 that encircles the motor disc I 8 is set to'its nominal maximum de ree of eccentricity relatively to the driven shaft 8.

when driving shaft I is rotated there will be no movement of pistons I8 in cylinders Ill because ring 28 is concentric with pump disc 8 and no turning moment will be exerted on ring 28.

to the pump disc and the motor disc.

-tion to. the stationary case arm 62.

to the rotatable casing 36.

Ring 28 and all parts connected to it, that is ring 34, rotatable case 38, 38, 3'! driving arm 82, valve 3 and driven shaft 8 will therefore remain stationary. The control position just described therefore corresponds to zero speed of driven shaft or a gear ratio of infinityzl, and there is no flow of working fluid.-

Adjustment of the control between the two nominal extreme positions mentioned above will give any desired ratio of driving speed to driven speed between 1:1 and infiiiityzl. In all intermediate positions of the control the centre of ring 28 will be on the right hand side of the vertical centre line in Figs. 2 and 3 and the centre of the ring 34 will be on the left hand side of the same centre lines and some working fluid will flow in a closed circuit between the pump cylinders I8 and the motor cylinders I8.

The driven shaft 8 may be caused to revolve in the reverse direction to that of the driving shaft I by moving the control beyond the setting required for zero speed of the driven shaft. In this position the ring 28 will have a slight eccentricity and the ring 34 a large eccentricity relative to the centre of the shafts land 8 and the centres of both rings will be on the left hand side of the vertical centre line in Figs. 2 and 5.

The driven shaft 8 may be caused to revolve faster than the driving shaft I and in the same direction by moving the control beyond the setting required for the 1:1 ratio. In this position the ring 28 will have a large eccentricity and the ring 34 a small eccentricity relative to the cen- 'tres of the shafts I and 8 and the centres of both rings will be on the right hand side of the vertical centre line in Figs. 2 and" 5.

In another form of construction according to the invention and as illustrated by Figs. 6 to 9 and 12, 14 and 15 the retaining rings 24 and 32 are positioned at opposite sides of the pump disc 8 and motor disc I5 by discs 24 that are secured The retaining rings 24 are free to move between the discs 24 and the pump disc and motor disc. The bush I4 is formed at one end with-a flange I4 that engages in a recess formed in the motor disc I5 and the other end is threaded to take a nut I4 which is screwed on to the bush to clamp .the motor disc I5 in a fixed position against rota- The drive is transmitted to the driven shaft 8 by means of a pin 39 which engages in a hole in the driving The hole is made slightly larger in diameter than that of the pin so that a driving contact is made but the loads due to the reactions of the pistons on the eccentric rings are not transmitted to the valve 3 or the driven shaft 8.

In the apparatus shown in Figs. 6 to 9 the pin '48 is formed with a collar 8| and such collar is formed with an inclined slot 82 that engages an inclined projection 83 on a block 84 that is fixed The pin 48 projects through an'opening 4| in the front cover 35 and is adapted to be moved endways by connection to the arm 42 that projects from the sleeve 43 that is slidably mounted on the tubular boss 44 'formed'on the front cover 35' of the rotatable casing 38, Fixed on the tubular member 43 is a ball bearing 48, and the outer member 48 is fixed in an internally threaded sleeve 88 that is slidably mounted in a boss 88 in the stationary case II. The sleeve 88 is fitted with a key 81 that engages a keyway 88 in the boss 88. The internally threaded sleeve 88 engages a flanged externally threaded member 88 that is fitted with a ball bearing 88 which is fixed on the pump shaft I. The screwed member 88 is fixed to the disc 8| that is formed with a cylindrical portion 82 which is fitted with a. cover 88 which covers a fan 84' that is fixed on the shaft I. The cover 83 is fixed to the cylindrical portion 82 by means of handles 85 which are screwed through the cover into the cylindrical portion 82. This casing is fitted with a graduated ring 88 for use with a pointer 81 that is fixed to a cover 88 that is attached by screws 88 to the stationary casing 5|. To cool the apparatus the fan 84 draws air through a hole I88 in the cover 83 which passes through openings I8I in the disc 8| and passes around the boss 86 inside the cover 88 along the outer surface of the stationary case 5| and between fins or vanes I82. When the externally threaded member 88 is turned the sleeve 43 is moved in an endwise direction, the slot 82 travels along the inclined projection 83 and a turning movement is imparted to the arm 42 relatively to the rotatable casing 35, 38 and 31 and adjusts the eccentricities of the rings 26 and 34 in relation to the axis of the driving shaft I and the shaft 8.

Referring to Figs. 10 and 11 which show a form of construction employing pump and motor of the vane type the form of control and general construction are the same as that illustrated in.

Figs. 6 to 9 and all parts common to both forms of construction are marked by the same reference numbers.

The pump disc 8 is formed with a number of radial slots I8 in which vanes I8 are free to slide.

The outer case of the pump is formed of three' parts, a body I5 and two covers I6 fastened together so that the pump disc 8 isfree to slide between the covers I8.

The spaces between each adjacent pair of vanes ID are bounded by the two covers I8, the

pump disc 8 and the body of the outer case I5 and are connected to ports II in valve casing 2 by radial extensions of these ports through the pump disc 8.

The body of the outer case I5 is supported by rollers II which engage an outer race in the ring 28.

The motor unit is constructed in a similar manner, the reference numbers being, motor disc I5, slots I8, vanes 21, body of outer case I8, flanges of the outer case I8, rollers 88, outer race 33 of the roller bearings, and ring 34.

Instead of rollers 11 and 88 hearing directly on the bodies I5 and I8 of the outer cases, complete ball or roller bearings may be used, the inner races being fixed to the bodies of the outer cases I5 and I8 and the outer races housed in the rings 28 and 34.

In another form of construction the pump unit may be of the piston type as shown in Figs. 1, 2, 5, 6 and '7 and the motor unit may be of the vane type as shown in Figs. 10 and 11, or alternatively, the pump unit may be of the vane type as shown in Figs. 10 and 11 and the motor unit may be of the piston type as shown in Figs. 1, 2, 5, 6 and '1.

In any form of construction the loss of working fluid from the system may be made up either by a small auxiliary pump driven from any rotating part of the gear, by gravity from an overdriven shaft 8.

head supply or by suction of the gear itself from a reservoir formed in the stationary case.

The base of the stationary case 5| acts as a reservoir for the working fluid, the level of which is such that no rotating part of the gear is submerged, or alternatively the rotating parts may be partially or completely submerged in the working fluid. Any convenient means may be employed for cooling the latter and means may be provided for obtaining complete or partial running balance at all speeds.

When the gear is to be used to give a reverse movement of the driven shaft 8 or when the gear is to be capable of being driven in either direction, either of the two passages l1 and II in the distributing valve 3 Fig. 13 may be .the suction passage and in this case both of these passages H and i8 may be made to communicate with the port through which the replenishing fluid is fed by means of lateral passages 63 formed in the These lateral passages may be of the alternative forms shown in full and dotted lines in Fig. 13.

Ilhe passages H and I8 are fitted with nonreturn valves 13 so that the passage which contains working fluid under pressure is automatically isolated from the lateral passage 63.

Either one or both of the passages l1 and I! in the distributing valve 3 may be fitted with relief valves l4 spring loaded to open at a pressure in excess of the normal working pressure to ensure that the working parts will not be damaged if the.

gear is overloaded.

The gear may be fitted with external reversing gear of any known type.

Packing rings may be fitted to prevent leakage between the distributing valve 3 and the valve casings 2 and Hi.

The capacities of the pump and motor cylinders may be equal or unequal, the ratio of the capacities depending on the output torque required at various speeds.

What I claim as my invention and desire to secure by Letters Patent in the United States is:

l. Hydraulic variable transmission mechanism comprising in combination a driving shaft and a driven shaft, a pump body driven by the driving shaft, a single set of radially movable members slidabiy mounted in the pump body, a sta-- tionary outer casing enclosing all the working parts, a stationary motor body arranged in rigid connection with the stationary outer casing, a single set of radially movable members slidably mounted in the motor body, a single eccentric member for causing the radially movable members of .the pump to reciprocate, a single eccentric member for controlling the reciprocation of the radially movable members of the motor, a rotatable case in which the eccentric members are pivoted, bearings supporting said rotatable case, a driving. member for driving the driven shaft from the rotatable case, eccentric adjusting means, means for adjusting the eccentricities of the eccentric members simultaneously so that when either eccentric member is concentric with the axis of the driving and driven shafts the other eccentric member is in an eccentric position with respect to the axis of the shaft, a distributing valve in the driven shaft having four ports formed in it consisting of pump and motor inlet and outlet ports, the pump inlet port being connected with the motor discharge port and the pump discharge port :being connected with the motor inlet port by passages within the valve, the motive fluid discharged by the pump actuating the radially movable members of the motor in accordance with the adjustment o'fthe eccentrics, and a passage for the replenishing of the working fluid in communication with the pump inlet port of the distributing valve.

2. Hydraulic variable transmission mechanism according to claim 1 in which the rotatable case is formed at oneend with a boss, an axially adjustable control sleeve slidably mounted on such boss and formed with a radial arm, a control pin operatively connected with the two pivoted eccentric members and with the radial arm, a member attached to the rotatable case having inclined surfaces, said radial arm having inclined surfaces which cooperate with the inclined surfaces on the member attached to the rotatable case to simultaneously adjustwith respect to the shaft the eccentricities, and means for axially adjusting the control sleeve.

3. Hydraulic variable transmission mechanism according to claim 1 in which the rotatable case is formed at one end with a boss, an axially adjustable control sleeve slidably mounted on such boss and formed with a radial arm, a control pin attached to the radial arm and slida'ble in holes formed in the two pivoted eccentric members, a member attached to the rotatable case having inclined surfaces and a collar on the control pin having inclined surfaces which engage the inclined surfaces on the member that is attached to therotatable-case to simultaneously adjust with respect to the shaft the eccentricities, and means for axially adjusting the control sleeve.

4. Hydraulic variable transmission mechanism according to claim 1 in which the rotatable case is formed at one end with a tubular boss. an axially adjustable control sleeve slidably mounted thereon and formed with a. radial arm, a control pin attached to the radial arm and slidable in holes formed in the two pivoted eccentric members. a member attached to the rotatable case having inclined surfaces and a collar on the control pin having inclined surfaces which engage the inclined faces on the member that is attached to the rotatable case to simultaneously adjust with respect to the shat-t the eccentricities, a :ball bearing comprising an inner race and an outer race and a ring of balls, the inner race being fixed on the axially adjustable control sleeve. an endwise movable sleeve fixed on the outer race of the said ball bearing which acts in the dual capacity of a journal bearing for the rotatable case and a thrust bearing for the axially adjustable control sleeve, and means connected with the endwise movable sleeve for axially adjusting the control sleeve.

MAURICE CARTER. 

